NL1009755C2 - Gas compressor. - Google Patents

Description

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GAS COMPRESSOR

Gas compressors are known in many embodiments. It is an object of the invention to provide a gas compressor that combines superior performance with an essentially simple construction, paying particular attention to efficiency and low noise production. i

In connection with the above object, the invention provides a gas compressor of the type specified in claim 1.

Now follows an introduction with regard to the new rotation device used in the gas compressor according to the invention.

Rotary devices are known in many embodiments.

It is known, for example, a centrifugal pump with an axial inlet and a liquid to be pumped radially under the influence of centrifugal forces with a rotor swinging outwards with blades and one or more, for example, substantially tangential outlets. Furthermore, an axial compressor with groups of rotor and stator blades arranged in cascade is known.

The structure contains many thousands of extremely complex - shaped parts, which also have to meet high requirements of - dimensional accuracy and mechanical strength.

An example of this is a gas turbine, in which in this case gaseous medium is released under pressure from a source intended for this purpose and is aimed at the vanes of a rotor, such that this rotor is driven with force voor- for, for example, rotating 3. 0 driving a machine, such as an electric generator.

These known devices exhibit flow instabilities, especially at low flow rates. -

These often cause an imbalance in the rotor load, which gives rise to heavy vibrations, uncontrollable speed variations and very heavy mechanical loads on bearings, shafts and blades.

All known rotary devices have still further technical shortcomings.

For example, the efficiency is often relatively low and strongly dependent on the speed.

In addition, the known devices are usually bulky, heavy and expensive.

When using casting techniques to produce a rotor, the blades must have a certain minimum wall thickness, which gives rise to undesired decreases in the effective flow volume and losses due to loosening and wake formation. In addition, the blade wall thickness and the necessary blade shape limits the number of blades to be accommodated. Furthermore, the casting technique inevitably leads to undesirable surface roughness and unbalance due to unintentional and uncontrollable density differences, for example due to inclusions.

Furthermore, the tensile strength of cast metals and alloys is limited.

Known centrifugal pumps further suffer from so-called slip, the phenomenon that the flow is poorly attached to the suction side of the flow channel, which is bounded by neighboring vanes. Due to the angle of expansion between the blades, there is a slip area or an area with "dead water", in which there is a large-scale stationary vortex, so that the flow in that area is zero. As a result, the output pressure of the centrifugal pump is highly pulsating.

Known devices are furthermore constructed in such a way that they produce a lot of noise during operation. All known devices operating as, for example, a water pump, have a limited pressure capacity. For example, for applications such as a rö fire brigade pump, pumps are often placed together in i ft O <- r · I UÜÖ / Ot) 3 cascade to achieve the required pressure, also expressed as the head of the water to be pumped.

In the known rotary devices it is furthermore sometimes experienced as a drawback that medium inlet and medium outlet do not show the same direction, but are for instance perpendicular to each other. Under certain circumstances it may be desirable, at least to have the ability, to direct the input and output in the same direction.

Known devices are furthermore unable to work with media of widely varying viscosities.

In known devices, the

15 flow rates of the flowing media during the I

flow through an establishment varies widely. As a result of the accelerations occurring, z noise production and loss of efficiency occur. In this connection, it would be desirable to keep the flow rate of flow-through medium through a rotary device the same, for example, within a range of z 0.2-5 x a guideline value under all conditions.

It is an object of the invention to provide a z gas compressor with a rotary device, which does not or at least to a lesser degree have the above-mentioned problems and limitations of the prior art. -

It is a further object of the invention to provide a gas compressor which is controllable over a working range which is greatly increased compared to the prior art.

Claim 2 relates to a preferred embodiment.

A very practical embodiment is specified in claim 3. The check valve is r ;; 35 inexpensive to manufacture and exhibits high reliability and long service life.

Claim 4 describes in general terms a possible form of the rotor channels. _

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Claims 5, 6 and 7 give increasing preferences for the number of rotor channels.

Claim 8 concerns a construction of the rotation device, which counteracts strong periodic pressure pulses during operation. Such a construction ensures a quiet and even flow.

Claim 9 concerns the use of an inlet propeller in the medium inlet at a rotary device that serves as a medium pump. The inlet propeller ensures that the medium enters the rotor channels without release with a certain pressure and speed.

A very practical embodiment, which concerns a light and easy-to-manufacture rotor, is described in claims 10 and 11.

Since it is important that there is no discontinuity in the region of the third medium throughput that could give rise to large-scale vortices and turbulences, detachment and noise production, the structure of claim 12 may be advantageous.

Claim 13 relates to a construction of the rotation device, in which a relatively large number of partitions can be used, without the thickness of the partitions 25 at the location of the third medium passage substantially reducing the passage for medium there at the location. As a result of the transverse dimension widening in the radial direction relative to the axial direction of the rotor channels, extra space is available for the interlaced placing of a second group of second partitions at a distance from the third medium throughput. Insofar as necessary, a third group of partitions can be placed between the interwoven placed first and second partitions. These baffles, in turn, are shorter than the second baffles and extend in the direction of the third to the fourth media passages from the end of the second baffles facing the third media pass to the fourth media pass. This construction: 1009? 55 ί

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allows very good flow conduction without essentially affecting the effective passage of the medium.

Claims 14 and 15 concern the shape of the 5 stator blades. Since all stator blades are angularly equidistant, their spacing is always the same in any axial position. Rheologically, however, it is essential that, seen in the direction from the fifth medium throughput to the sixth medium throughput, effective fanning occurs in a direction viewed along a flow line in a stator channel. Perpendicular to such a flow line, a run angle can be defined at any position along this flow line between the blades. It is this angle to which claim 14 relates. The structure of claim 15 has the advantage of a significantly improved efficiency.

The use of sheet material for the production of the dishes and the blades according to claim 16 has the advantage that the rotor can be very light. Sheet material can also be very light, smooth and true to size. The choice of material will be further determined by considerations of abrasion resistance (depending on the passing medium), bending stiffness, mechanical strength, and the like. It is important for the rotor, whose trays have the described double-curved shape, that the main shape is preserved, even if the material is subjected to centrifugal forces due to high rotational speeds.

30 In this regard, attention is drawn to the fact that the vanes, which are arranged between the plates and "rigidly coupled thereto", contribute significantly to the stiffening of the rotor. For this reason, too, it is important , use a large number of blades.

A rotor with very high dimensional accuracy and 1 = negligible intrinsic imbalance can also be manufactured.

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Claims 17, 18 and 19 provide options regarding material choices under specific conditions.

Depending on the dimensions of the rotor and the speed, the described sheet material can have a desired value. In general, a suitable choice lies in the range indicated in claim 20. The moment of inertia of the rotor is preferably as small as possible in view of the possibility of a small unbalance, in particular with low density media, such as gases. In this connection it is preferable to choose the technically smallest possible thickness.

Claim 21 describes some possible techniques with which the rotor baffles can be coupled to the dishes.

Claim 22 concerns the possible material choices for the stator blades. Broadly speaking, the technical considerations underlying this choice are the same as for the rotor bulkheads.

Claim 23 concerns the material choices of at least the materials on the inner surface of the housing and of the stator blades, respectively. By equating the thermal expansion coefficients of these materials in accordance with claim 23, thermal stresses are avoided and it is ensured that the interconnection and the correct shape of the stator channels are maintained even in the case of extreme temperature variations.

In this connection, the use of thin sheet material for the blades also has the advantage that thermal stresses are effectively avoided.

Claim 24 indicates as specific elaboration of the described technical principle the possibility that the materials are the same. It will be clear that in a further elaboration, not only the cylindrical inner surface of the housing can be of the material in question, but that this may apply. I U U b j u

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for the entire cylindrical shell of the house, or even the entire house.

Claim 25 focuses on the shape of the stator channels. As already described above in connection with claims 16-20, the mass moment of inertia and hence the chance of a certain impeller imbalance is preferably as small as possible.

Claim 26 relates to the same aspect and applies in particular to gas as a medium, which after all makes no significant contribution to the moment of mass inertia. Although, due to the small radial dimensions, the shaft should have a considerable weight to have a moment of mass inertia in the same order of magnitude as that of the rotor, it should be understood that the contribution in question may be substantial in connection with the relatively long length of the shaft under conditions. Furthermore, the rotor will preferably be made as light as possible, so that on that ground its moment of inertia will also be relatively small.

Claims 27 and 28 give some possibilities for forming the rotor plates.

Claim 29 focuses on a very specific method of forming a rotor.

The structure according to claim 30 is particularly important in the case of a very hot or very cold medium.

Claim 31 focuses on a very advantageous embodiment in which an effective sealing is

combined with almost zero friction. H

Claims 32 and 33 increasingly show possible numbers of stator blades. In the design of the rotary device according to the invention, it should be taken into account that a local flow tube can only be controlled over a wide flow range if the flow tube is elongated.

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Claims 34, 35 and 36 further characterize the rotary device in terms of the ratio between the total cross-sectional area of all fourth medium passages and the third medium pass. The choice in question strongly depends on the design requirements.

Analogously, claims 37, 38 and 39 give possibilities with regard to the ratio between the diameter of the crown of fourth medium passages and the diameter of the third medium passage. The choice in question depends on the pressure ratio to be generated between the inlet and the outlet in the case of a pump or the expansion ratio in the case of a turbine.

In the gas compressor according to the invention there is still strong rotation in the region of the fourth and the fifth medium passages. This results in a locally relatively low static pressure, in contrast to the known centrifugal pump. As a result of the relatively low local pressure, relatively small requirements are imposed on the thicknesses of the walls concerned and on the local seals, as a result of which use can be made, for example, of simple seals, such as labyrinths, which are considered low-quality under certain circumstances. seals. It is well known that a labyrinth seal is not completely closed by its nature. However, due to the relatively low local pressure, the seal is sufficient when using labyrinth seals.

The said small wall thicknesses allow manufacture with deep drawing.

The device according to the invention is very versatile. As a pump, it exhibits a very flat pressure and efficiency characteristic and a more or less monotonic power characteristic, which means that one pump is suitable for many very diverse applications, while 3 different sizes are required for conventional pumps for different applications.

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The said monotonic, substantially linear characteristics at any speed offer the important possibility of achieving a substantially unequivocally corresponding output performance by means of a very simple control of the driving power. The state of the art requires complicated and expensive control for this, based on the instantaneous values of a number of relevant parameters. This is the reason why such schemes are not applied in practice.

For pumping media with very different viscosities, only a limited number of different dimensioned pumps is also necessary due to the low dependence of the device properties on the viscosity of the medium.

When used as a pump, one rotary device I

a very high flow rate and / or a very high pressure

comparable to cascading an I

20 number of pumps according to the state of the art.

To reverse the operation of a pump I

to a motor or vice versa, generally some adjustment of the sizing of stator channels and rotor channels will be desired.

The invention will now be elucidated with reference to the annexed drawings. In the drawings: figure 1 shows partly in cross-section, partly in cut-away side view, a first embodiment of a rotary device; = Figure 2 shows a partly broken away perspective view of the device according to figure - 1, which is schematized for the representation of the spatial structure; figure 3 shows a variant of a manifold; = Figure 4 is a partly broken away perspective view of a second embodiment of a rotation device; 1 C C V J "" Figure 5A is an exploded view of a part of a stator with stator blades bounding stator channels; figure 5B shows an exploded view of a stator vane; figure 5C shows a view corresponding with figure 5A of two stator blades for explaining the geometric proportions; figure 5D shows a rectilinearized view of the stator channel according to figure 5C; figure 5E is a graph of the channel width as a function of the channel distance; figure 5F shows the included angle as a function of the channel distance; Figure 6A shows a schematic cross section of a third exemplary embodiment of a rotary device; figure 6B shows a view corresponding with figure 6A of a variant.

Figure 7 is a perspective exploded view from the bottom of the internal structure with rotor and stator of a fourth embodiment of a rotary device, with the housing and the lower rotor plate omitted; Figure 8 from the top of the stator according to figure 7, with the housing and rotor omitted; figure 9 is a perspective exploded view from below, corresponding to figure 7, of the rotor; Figure 10A shows a perspective view corresponding with figure 8 of the stator part of a fifth exemplary embodiment, wherein the manifold is designed differently; figure 10B shows a view corresponding with figure 10A of a variant; figure IOC shows a view corresponding with figure 10B of a variant; 1009755

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Figure 10D is a graphical representation of the relationship between the tangential distance between two blades and the axial position; Figure 10E shows the channel width as a function of the channel position; Figure 10F is a graphical representation of the included angle as a function of the channel position; figure 11 shows a partly broken away perspective view of a part of a sixth embodiment of a rotary device; Figure 12A is a partial schematic perspective view of a die for forming rotor blades; figure 12B shows a cross-section along the line 15 B-B in figure 12A; Figure 12C is a schematic exploded view of a device for manufacturing a stator vane; figure 12D shows a perspective view of the device according to figure 12C;

figure 13A shows a highly schematic exploded view of a device for assembling a T

rotor according to figure 9; figure 13B shows a schematic partial perspective view of an arrangement of a number of guide blocks in the manufacturing phase of a stator; - ------ Figure 13C shows a partly broken away perspective view drawn under figure 13B of the stator manufactured according to figure 13B; figure 13D shows an assembly of heat and electricity conducting blocks according to figure 13B; Fig. 14 is a schematic graph comparing the efficiency as a function of the relative flow rate of a known rotary device and a device according to the present patent application; figure 15 shows the pressure to be generated by a device according to the invention as a function of the flow rate. · = 12 at different speeds compared to a known pump;

Figure 16 is a graphic representation corresponding to Figure 15 of another embodiment.

Figure 17 shows a perspective view of a further embodiment of the rotation device according to the invention; figure 18 shows a cut-away perspective view of the device according to figure 17; Figure 19 shows an exploded view of the device according to figure 17; figure 20 shows a perspective view of the motor; Figure 21 is a perspective view of the flow channel unit extending between the sixth medium throughput and the second medium throughput; and figure 22 shows a top view of the unit according to figure 21.

Figure 23, in longitudinal section partly in side view, a two-stage compressor according to the invention.

Figure 1 shows a rotation device 1. It comprises a housing 2 with a central, axial first medium feed-through 3 and three axial second medium feed-throughs 4, 5, 6. Furthermore, the device 1 comprises a housing located in said housing 2 and outside that housing 2 extending shaft 7, which is rotatably mounted with respect to the housing 2 and carries a rotor 8 accommodated in the housing 2, which will be specified hereinafter. The rotor 8 connects with a central third medium passage 9 to the first medium passage 3. The third medium passage 9 branches into a number of angularly equidistant rotor channels 10, each of which extends in a respective, at least more or less radially main plane, from the third medium passage 9 to a respective fourth medium passage 11. The end zone of the third medium passage 9 and the end zone of the fourth medium passage 11 each extend substantially in axial direction. As shown in Figure 1, each rotor channel 10 has a generally faint S shape, roughly corresponding to a half cosine function, and has a center portion 12 extending in a direction with at least a significant radial component. Each rotor channel has a cross-sectional area that extends from the third medium throughput to the fourth medium throughput.

Furthermore, the rotation device 1 comprises a stator 13 accommodated in the housing 2. This stator 13 comprises a first central body 14 and a second central body 23.

The first central body 14 has on its zone adjoining the rotor 8 a cylindrical outer surface 15, which, together with a cylindrical inner surface 16 of the housing 2, has a generally cylindrical medium passage space 17 with a radial dimension of at most 0.2x the radius of the cylindrical outer surface 15, in which medium passage space 17 is accommodated a number of angular equidistant stator vanes 18 bounding pair stator channels 18, which stator vanes 19 each form a substantial, in particular at their end zone 20 directed towards the rotor 8, a fifth medium passage 24 have a direction at least 60 ° from the axial direction 21, and at their other end zone 22 forming a sixth medium passage 25 have a direction slightly different, in particular at most 15 °, from the axial direction 21, which fifth medium passages 24 connect to the fourth medium passages 11, and which sixth medium passages 25 in ve connection with the three second medium passages 4, 5, 6. - .....

The second central body is configured such that between the sixth medium passages 25 and 35 the second medium passages 4, 5, 6 three extend in the direction from the sixth medium passages 25 to the second medium passages 4, 5, 6 manifold channels 26 . These manifold channels are also defined by the outer surface 29 of the second central body 23 and the cylindrical inner surface 16 of the housing 2.

In Figure 1, a general medium flow path 27 is indicated by arrows. This path 27 is defined between the first medium throughput 3 and the second medium throughputs 4, 5, 6 through respectively: the first medium throughput 3, the third medium throughputs 9, the rotor channels 10, the fourth 10 throughputs 11, the stator channels 18, the sixth medium throughput 25 , the manifold channels 26, the second fluid passages 4, 5, 6, with substantially smooth transitions between said parts. It is noted that in figure 1 the flow of the medium according to arrows 26 is shown in accordance with a pumping action of the device 1, for which purpose the shaft 7 is rotatably driven by motor means (not shown). If medium through pressure mediums 4, 5, 6 were forcibly admitted into the second medium passages 4, 5, 6, the medium flow would be reversed and the rotor 8 would rotate due to the construction of the device 1 described below. driven, also under rotary drive of the shaft 7.

The structure of the device is such that there is. 25 a reciprocal force clutch exists during operation between the rotation of the rotor 8, and thus the rotation of the shaft, on the one hand, and the speed and pressure in the medium flowing through said medium flow path 27.

In general, therefore, the device 30 can act as a pump, in which case the shaft 7 is driven and the medium is pumped according to the arrows 27, or as a turbine / motor, in which case the medium flow is reversed and the medium provides the driving force .

Figure 2 shows the device 1 in a highly schematic exploded perspective. It is clear that the manifold channels 26 are formed by a second central body 23, which can be regarded as a

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15 insert located above the first central body 14 and having three recesses 30 forming the manifold channels 26. These recesses have rounded shapes and connect at their underside to the 5th medium passages 25 for guiding the medium according to arrows 27 to the second medium passages 4, 5, 6.

Figure 3 shows the insert 23 in partly broken away perspective view. In this arbitrary embodiment, the insert 23 is formed from sheet metal. However, it can also consist of other suitable materials, such as solid, optionally reinforced plastic and the like.

Figure 4 shows a device 31, which corresponds functionally to device 1. Device 31 comprises a drive motor 28.

As can be seen more clearly in Figure 4 than in Figure 1, an input propeller 32 with a number of propeller blades 33 is arranged in the third medium passage 9 serving as medium inlet.

In anticipation of the discussion of the rotor according to figure 9, which corresponds to the rotor 8 according to figure 1, it is already noted that the rotor 34 in the device 31 according to figure 4 has a number of additional stiffening braces 35 which are missing in the rotor 8 .

As shown in figure 9, rotor 8 comprises a number of separate parts, which are integrated with each other in a manner to be described below. The rotor 30 comprises a lower saucer 36, an upper saucer 37, twelve relatively long partitions 38 and twelve relatively short partitions 39 interwoven therewith, which in the manner shown form equidistant boundaries of respective rotor channels 10. The partitions 38, 39 each have a 35 curved shape and perpendicularly bent edges 40, 41 for medium-tight coupling with the dishes 36, 37. The partitions 38, 39 are preferably connected to the dishes by welding and thus form an integrated '7 7' U uc »f OO> - 16 ί rotor. The input propeller 32 is placed in the central third medium passage 9. This has twelve blades, which connect to the long rotor partitions 38 without a rheologically significant transition. In the center 5 of the input propeller 32 a downwardly tapering streamline element 42 is placed.

In particular figure 4 clearly shows the operation of the device 31 acting as, for example, a liquid pump. By driving shaft 7 with entraining 10 of rotor 34, liquid is forced into the rotor channels 10 by the action of propeller 32. Partly as a result of the occurring centrifugal acceleration, a strong pumping effect is obtained, which is comparable to that of centrifugal pumps. Centrifugal pumps, however, operate with fundamentally differently shaped rotor channels. The liquid flowing out of the rotor channels 10 exhibits a strong rotation and is in the form of an annular flow with both a tangential or rotational direction component and an axial direction component. The stator vanes 19 remove the rotational component and return the initially axially introduced flow axially into the manifold channels 26, where the partial flows are collected and supplied, respectively, medium outlets 4, 5, 6. If desired, the 25 in Figure 2 shown in a manner shown, by means of an association of the three outlets 4, 5, 6 into one pipe 43, the medium is further pumped via one pipe.

! Referring to Figure 10, it is noted that other embodiments are also possible, wherein the outlet 30 also extends in an almost exactly axial direction.

Figure 5A shows that the stator blades 19 have a bent edge 44 on their input side. This edge has a Theological function. It ensures a smooth, streamlined transition from the strongly rotating medium flow delivered by the fast-rotating rotor 34 to the stator channels 18.

The rotors described in this embodiment consist of stainless steel parts, with reference 17 to figure 9 the dishes 36, 37, the partitions 38, 39, the propeller 32.

Figure 5A shows in expanded form the outer surface 15 of the first central body and the 5 stator blades 19.

Figure 5B shows a view of a partition 19 according to the broken line B-Bin Figure 5a.

Figure 5 shows a set of stator blades 19 bounding a stator channel 18 together.

Figure 5β shows a deflection of the channel 18 with the determination of the mutual angles in accordance with the successive lines 46, which, as figure 5D shows, have all mutual distances along the axis of approximately 5 mm, at least in this embodiment. The spout width of each stator channel, as shown in Figure 5C, is approximately 15mm. Figure 5D shows the different positions with the associated half angles between the blades 19 at the indicated positions.

Figure 5E [shows the channel width as a function of the positions according to Figures 5C and 5D.

Figure 5F shows the included angle in accordance with the representation in Figure 5D. It is important to note that nowhere does this angle exceed the rheologically important value of approximately 15 ° and even remains below the value of 14 °.

It can be clearly seen in figure 1 and figure 4 that the respective rotors 8, 34 in the region of the third medium throughput and the fourth medium throughput with respect to the housing 2 are sealed by respective labyrinth seals 45, 46. The shaft is bearings relative to the housing by means of at least two bearings, only one of which is shown in Figures 1 and 4. This bearing is indicated by reference number 47.

Figure 6A shows a rotation device with a slightly different construction. In this structure, there is a continuous unit of manifold channels, since there is a space 49 passing through a second central body J-V. v · - J> 18 50 is bounded together with the wall 51 of the housing 52. Thus, there is only one medium discharge 4.

Figure 6B shows a rotation device 48 ', the construction of which corresponds almost entirely to the structure of the device 48 according to Figure 6A. Unlike in device 48, device 48 'includes an electric motor. It comprises a number of stator windings, indicated by the reference numeral 90, which are stationary, and a rotor armature 91, which is fixedly connected to the top plate 37 of rotor 8.

The connecting wires of the stator windings are not shown. They may very suitably extend upwardly through the unused space within the stator vanes 19 and exit the device 48 'at a desired suitable position.

Figure 7 shows the internal structure of rotor 8, leaving out the lower saucer 36. Reference is made in this connection to figure 9. Of importance in this figure is the construction of the second central body 53. In particular a comparison 2 illustrates in which this embodiment differs from the construction of device 1. The second central body 53 is provided with three inserts 54 which delimit recesses 55 which connect the outflow openings of the stator channels 18 to medium drains 4, 5, 6. The recesses 55 are provided with current-conducting partitions, which, although have different shapes, are all conveniently indicated by reference numeral 56 for convenience. Due to this construction I 30, a very calm swirl-free flow is also realized.

Figure 8 shows the stator 57 of Figure 7 from the other side.

Figure 10A shows part of a fifth embodiment. The stator 61 has a highly regular and symmetrical construction and differs in that from the embodiments which are particularly clearly shown in Figures 2 and 7. In the '1009755 19 embodiment of Figure 10A, manifold channels 62 on analog formed on the stator channels 18. The manifold channels 62 are delimited on the one hand by a surface 63 5 of a second central body 64 tapering in the direction of discharge 4 and on the other hand by the inner surface of a housing (not shown). The channels 62 are separated from one another by separators 65. As shown, on average about 2.7 stator channels unite into one manifold-channel 62.

Figure 10B shows a variant of Figure 10A. The stator 61 'of Figure 10B differs from the embodiment of Figure 10A in that the channels 62' are separated from each other by a plane 63 'and partitions 65' of different shapes than the respective parts in the stator 61. The As a result, the medium throughput 93 'of Figure 10B has a larger passage than the medium throughput 93 of Figure 10A. The speed difference across channels 62 'is therefore smaller than the speed difference across channels 62. Under circumstances this may be desirable.

Figure IOC shows a further variant, in which the stator 61 '' comprises not only the relatively long partitions 19, but also interposed shorter partitions 19 '25 interposed therewith. The effect of this will be explained with reference to Figures 10D, 10E and 10F below. Otherwise, the stator 61 '' substantially corresponds to the stator 61 '. It is pointed out that the lower end zones of the partitions 19 and 19 'are folded over.

This ensures a good streamline shape with increased stiffness, strength and erosion resistance.

Figure 10D shows the tangential distance between the adjacent partitions 19 and 19 'of Figure 10C and the partitions 19 of Figures 10A and 10B. The tangential distance is shown as a function of the axial position. Curves I and II correspond to neighboring bulkheads.

Figure 10E relates to the embodiment according to Figure IOC. The graph shows the channel width as 1008755 20 function of the channel position. The influence of the interwoven placement of relatively long and relatively short bulkheads is clear. This influence is recognizable by the jump in the graph. If this jump were not present, the part indicated by II would smoothly connect to the part indicated by I, as a result of which the channel width in the region II would increase substantially. This would greatly compromise the elongated nature of the stator channels and thereby affect the performance of the device 10 in question.

Figure 10F shows the included angle as a function of the channel position. A comparison with figure 5F shows that, due to the choice of the interwoven arrangement of short and long partitions, the enclosed angle which according to figure 5F is almost 14 °, in the structure according to figure 10C is always smaller than 10 °.

Figure 11 shows a sixth embodiment. The rotary device 66 includes a rotor 67 with a number of rotor channels 68 bounded by sheet metal walls 20. This rotor can be formed by explosive deformation, by internal medium pressure, by a rubber press or other suitable known techniques. Manifold channels 69 are delimited by approximately 25 helically extending baffles 70 in the drawn area.

Figure 12 shows how the spatially very complicated shaped stator blades 19 can be manufactured from respective strips of stainless steel.

Figure 12A shows very diagrammatically a mold 71 for forming a stator vane 19 from a flat strip of steel of a certain length. The mold comprises two mold parts 72, 73 which are rotatable relative to each other and which, in a closed rotational position 35, are two facing each other. have oriented interfaces, the shapes of which are substantially identical, which shapes correspond to the shape of a blade 19. The interface in question is located at 74 1 n 0 Q? In the position indicated, where, in accordance with reality, a blade 19 has been drawn in, in which the adjacent parts of the mold parts 72, 73 are shown broken away, in accordance with reality. On the underside, the respective interface 75 is visible, which continues according to the shape of the blade 19. Arrows 76 show the relative rotatability of mold parts 72, 73. Guide blocks 76, 77 serve as guidance of the mold parts 72, 73 during the rotation. The said means for rotary driving of the mold parts 72, 73 are not shown.

In the open position of the die, not shown in Figure 12A, a straight stainless steel strip is inserted. This strip is completely flat and straight.

The mold parts are then rotated mutually, such that the molding surfaces approach each other. As a result, the strip engages while simultaneously deforming it. In this regard, reference is made to Figure 12B, where the mold parts 20, 73, which interact with each other are shown. As will be clear, mold part 73 has a recess 78 on its underside adjacent to support cylinder 77 corresponding to the flanged bottom edge 79 of strip 19, while at the top a comparable recess 80 remains between the top surface of mold part 72 and mold part 73 when closing. of the mold cavity. The final closure of the mold cavity is determined solely by the thickness of the metal of blade 19. The recess 80 corresponds to the top flanged edge 81.

Figures 12C and 12D show an alternative device or die 871 for forming a stator vane 819 from a flat strip of steel 801 with the curved shape of certain length shown in Figure 12D. The die 871 comprises two relative to each other with force 35 rotatable mold parts 872, 873, which in a closed rotational position have two mutually facing interfaces, the shapes of which are substantially identical, which shapes correspond to the shape of a blade 819.

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The mutual rotation of said mold parts 872, 873 can take place by rotation of mold part 873 by means of handle 802, mold part 872 remaining stationary, because it is formed in one piece with a frame 803, which is attached to a worktop.

A second handle 804 is attached to a substantially cylindrical element 805 which has a more or less triangular opening 806 which serves to place strip 801 and take out a shaped blade 819. By means of a keyway 807 matching key 808, the respective parts 805 and 814 are coupled together for rotation.

Said interfaces 810, 811 serve to impart to strip 801 the double curved main shape, but without the flanged edges 812, 813 which serve to connect a blade deformation of a stator to respective cylindrical bodies. After this shape is obtained by rotation by means of handle 802, the flanged edges 812, 813 can be formed by a follow-up rotation by handle 804. During this follow-up rotation, the intended conversion of said edges takes place by rotation of central part 814, which as stated for rotation is coupled to element 805 and is provided with a conversion edge 815. A second conversion edge 816 is provided on the inside of element 805.

Thus, by a very simple operation with the device 871, a blade 819 can be produced from the preformed metal strip 801.

It is noted that strip 801 is made by laser cutting. This provides a very accurate and chip and burr-free sheet metal element, which is free from internal stresses. The narrowed end zone 820 can be bent in accordance with arrow 823 to the position indicated with 820 '35. Thus, blade 819 is ready to serve as part of a stator. Such a stator is shown, for example, in Figure 13C.

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Figure 13A shows a possible and very practical manufacturing method of rotor 8. It is assumed that saucer 36, upper saucer 37 and the rotor plates 38, 39 to be placed between them and to be bonded thereto (see also figure 9).

The exploded view according to Figure 13A also shows that the three-dimensionally formed partitions 38, 39 can accommodate chains of correspondingly shaped electricity and heat conducting blocks 82. These blocks are united by wires 83 to form respective chains and can serve to conduct the current, which can be passed through a top electrode 84 and a bottom electrode 85 through tray 37, blocks 82, baffles 38, 39, bottom tray 36 and bottom electrode 85, respectively. guided by an electrical supply 86. By means of pressing means (not shown), the dish-shaped electrodes 84, 85, the respective shapes of which correspond to top dish 37 and bottom dish 36, respectively, are pressed together with force under corresponding pressure of the said and in figure 3A spaced apart parts. Profiled zones 86 serving as pressure points are provided in top electrode 84. Corresponding zones 87 are arranged in the bottom electrode. During the passage of a sufficiently large current, a large current will be passed through the relevant flow path via the pressure zones 86, 87, which are registered with the partitions 38, 39. This effectively spot welds the bulkheads 30, 38, 39 to dishes 36, 37. The copper blocks 82, for example, are essential for good current conduction without detrimental thermal effects to the partitions 38, 39. After a spot welding operation has thus been completed, the respective chains of blocks can be removed by pulling on the wires 83. After this operation, the rotor is in principle ready. As Fig. 1 shows, a mounting disc 90 can be welded to top plate 37. With cap 91 it forms the fastening of the rotor to shaft 7. After the spot welding operation as described above, the rotor according to figure 4 is provided with braces 35, after which shaft 37 is fastened.

Figure 13B shows greatly simplified and with some parts omitted an arrangement 830 for manufacturing a stator 831 as shown in figure 13C. For a good understanding of the arrangement according to figure 13B, reference is first made to figure 13C. The stator 831 comprises a cylindrical inner wall 832 and a cylindrical outer wall 833. In this embodiment, these walls are made of stainless steel. The outer wall 833 is relatively thick, while the inner wall 832 is relatively thin. The relatively long length stator vanes 819 (see Figure 12) and the interlaced interlaced vanes 819 'of shorter length are placed in the desired position and are welded with the flanged edges 812 and 813 to inner wall 832 and outer wall 833, respectively. It will thus be appreciated that the shapes of these flanged edges 812 and 813 must adhere precisely to the respective cylindrical surfaces. The devices shown in Figure 12 are specially designed thereon.

Figure 13B shows, with the omission of cylinders 832, 833, an arrangement of equidistantly placed chains of copper blocks, all of which are conveniently designated 834 and which have the shape shown in Figure 13D, corresponding to the shape of 30 blades 819 and 819 respectively ". The blocks are mechanically connected to each other and electrically separated from each other by means of a lace 835. A rubber pad 836 has such a shape that the overall structure 837, consisting of blocks 834, lace 835 and pad 836,35, fits snugly between the blades 819, 819 'of a stator 831. The blocks 834 have a general U shape . This allows the edges 812, 813 to be electrically conductive and thermally conductive connected to each other, without the electrical conduction taking place via the center plate of a blade 819. Comparison of Figures 13B and 13C shows the relative placement of blocks 834 and blades 819, 819 '.

Figure 13B is shown simplified in that only the front group of chains 837 is shown, while, moreover, the cylindrical jackets 832, 833 are omitted for clarity. An outer electrode 838 is placed outside the outer jacket 833, while an inner electrode 839 is placed inside the inner jacket 832. These electrodes are adapted to simultaneously pass currents through spot welding zones, all of which are conveniently designated 840. For this purpose, the electrodes 838, 839 are connected to a current source 841. After arranging the blades 819, 819 'with interposition of the chains 837 over the entire circumference with placement of both inner cylinder 832 and outer cylinder 833, the inner electrodes 839 and outer electrodes 838 are placed, after which the current passage 20 is effected, which results in that at the flow passage points the flanged edges 812, 813 are spot welded to inner cylinder 832 and outer cylinder 833. Then, the respective chains 837 at the top of laces 835 are pulled out of the structure, after which the stator 831 is ready.

Figure 14 shows a graphical representation of the efficiency "EFF" expressed as a percentage as a function of the relative flow rate Q of a prior art device, respectively (Graph I), as measured on a device of the above-described type of FIG. 1 (graph II) and finally according to figures 7, 8, 9, 10. It will be clear that the yield curve of the structure according to the invention is substantially higher than that according to the prior art and shows a considerably flatter course. In particular, the improvement at lower speeds is spectacular. This improvement explains that one device for many very j <J v i.

26 different applications can be used. The prior art often requires different devices for different applications.

Figure 15 also shows the performance of a device according to the invention which functions as a pump. The graphs drawn in figure 15 relate to the pump pressure as a function of the flow rate of a device according to the invention, in comparison with an eight-stage standard-centric centrifugal pump with a dimensioning which is comparable to the dimensioning of the device according to the invention. The graph I indicated with circular measuring points concerns the measurement on a known pump NOVA PS 1874. The other graphs concern measurements on a pump according to the invention with the following speeds, respectively: 1500, 3000, 4000, 5000, 5500, 6000 revolutions per minute .

Figure 16 shows measurement results in a comparison between two types of pumps according to the invention and two types of pumps according to the prior art. Graphs I and II relate to a conventional type eight-stage centrifugal pump at 3000 rpm. Graph I concerns an inlet of 58mm while graph II concerns an inlet of 80mm.

The drawn graphs with indications 25, 1500, 3000, 4000, 5000, 6000 revolutions per minute, respectively, relate to a one-stage device according to the invention with a housing of 170mm diameter, a rotor diameter of 152mm and an inlet diameter of 38mm. The graphs drawn with broken lines 30 also relate to a one-stage device according to the invention with a housing with a diameter of 170mm, a rotor diameter of 155mm, and an inlet diameter of 60mm.

Lines III and IV respectively indicate the respective cavitation limits of the first type of pump according to the invention as described and the second type of pump according to the invention as described.

1 η n p 7 5 ς

I W V- · i \ J \ J

27

From the foregoing, it can be seen that the described new structure of a rotary device produces substantially better results than comparable known devices. With particular reference to Figures 5 and 16, it is again pointed out that the comparisons relate to a one-stage device according to the invention and an eight-stage device according to the prior art, i.e. eight in cascade-switched known rotary devices. Figure 17 shows a unit 901 comprising a rotation device 902 and a motor 903. The unit is designed to operate as a pump. At the bottom there is a first medium feed 904 serving as an inlet and on the side there is the second medium feed 905 serving as a discharge.

Figure 18 schematically shows the construction of the unit 901. Contrary to the embodiment according to, for example, figure 4, in which the unit consists of a motor and a pump connected in principle inseparably, the unit 901 is composed of two separate components. To this end, the motor shaft 906 has an outwardly tapering end with a conical thread 907 at the end, while rotor shaft 908 has a corresponding complementary shape. In this way, motor 903 and pump 902 are releasably coupled and transmitting forces, yet a very easy releasability is nevertheless ensured. In particular, the structure of a part of pump 902 will be discussed below with reference to Figures 21, 30 and 22.

Figure 19 shows, in exploded view, how the main constituent components are interconnected and interrelated. It is important to note that the top component 909 of pump 902, in which the stator is located, is constructed differently from the respective parts in the above-described and shown embodiments. Rotor 910 Λ Γι ·. · ·: ^ 'J / j j 28 (and input component 911 correspond to the previously described versions.

Figure 20 shows motor 903 with a coupling piece 912 at the bottom for coupling with a corresponding coupling sleeve 913 to output component 909.

Figures 21 and 22 show a part 914 of output component 909. Part 914 includes a sheet metal funnel 915 with a central opening 916.

In the funnel 915, current-conducting baffles are arranged against the wall, which are arranged in the manner shown in Figs. 21 and although they have different shapes, but for convenience all are indicated with the reference number 917. The bulkheads 917 are members of one parametric family.

Inside the funnel 915 there is an inner funnel 918, also of sheet metal, such that the current conduction partitions 917 are bounded by the respective funnels 915 and 918 and thus form current conduction channels 919. These 20 conduction channels 919 all open into drain 905 and ensure a controlled flow pattern with very low friction losses. The flow conductor baffles 917 may be fabricated in a manner related to the manner in which the stator blades and / or the rotor baffles can be fabricated. With regard to possible manufacturing methods, reference is made in this regard to Figures 12 and 13.

The structure of unit 901 need not be discussed further. On the basis of discussion 30 of the previous exemplary embodiments, both construction and operation will be clear.

Functionally, the current conduction channels 919 correspond to the manifold channels 62 and 62 'of Figures 10A and 10B, respectively. Contrary to Figure 10, the structure of unit 903 is such that drain 905 extends to the side of unit 903. This simplifies the construction of the critical coupling between motor 903 and pump 902. It should be noted that the design according to, for example, Figures 1, 2 and 4 could also be used in this connection.

Figure 23 shows a gas compressor (501) according to the invention. The gas compressor includes a housing (502) with a gas inlet (503) and a gas outlet (504). The housing (502) contains a first compression space (505) with a first inlet (506) and first outlet (507), as well as a second compression space (508) with a second inlet 10 (509) and a second outlet (510) . Furthermore, a first gas pump (511) is accommodated in the housing with a first pump inlet (512) connecting to the gas inlet (503) and a first pump discharge (513). This is built up as one unit with a second gas pump (514) with a second pump inlet (515) and a second pump discharge (516). A first annular check valve (522) is arranged between the first pump discharge (513) and the first inlet (506), while a second check valve (523) is arranged between the second pump discharge (516) and the second inlet (509).

The basic structure of the integrated gas pumps (511,514) corresponds to that shown in, for example, Figures 1, 2 and 4 and will therefore not be discussed again.

The device (501) deviates from the devices described above in that the rotor (517) and the stator (518) of the rotary device (501) are designed in concentric relationship to be double, via two respective gas passageways ( 519,520), a first gas stream (519) from the first pump inlet (512) to the first inlet (506) and a second gas stream (520) from the second pump inlet (515) to the second inlet (509). The rotor shaft (420) is drivable by a motor, which in this embodiment is integrated with the device (501) 35 and is housed in housing (502).

During rotary drive under the influence of motor (525), air (531) is drawn in via gas inlet (503). This air travels through the track (519) and enters a significant pressure increase through the first inlet (506) into the first compression space (505) under the pressure. From this space (505) it is sucked in through the second pump inlet (515) into the second gas flow path (520) into the rotor (514) and enters through the second inlet (509) under even more increased pressure into the second, smaller compression space ( 508), which it can exit via second discharge (510), which is concentric with rotor shaft (524) and extends outside the housing (502).

10 The two-stage compressor (501) exhibits superior characteristics and is virtually silent.

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Claims (39)

1 G 0 S? 5 extend more or less radially main plane from the third medium throughput (9) to a respective fourth medium throughput (11), the end zone of the third medium throughput (9) and the end zone of the fourth medium throughflow (11) each extending substantially axially and each rotor channel (10) has a curved shape, for example a general U-shape or a general S-shape, has a middle part (12) that extends in a direction with at least a substantial radial component, and each rotor channel ( 10) exhibits a flow tube cross-sectional area, i.e., a cross-sectional to each local main direction, which increases in the direction from the third medium throughput to the fourth medium throughput from a relative value of 15 to a relative of at least 4. ( c) a stator (13) accommodated in that housing (2), comprising: (c.1) a first central body (14) which has a substantially rotationally symmetrical, for example at least 20 more or less cylindrical, at least Ans has a more or less conical, curved or hybrid shaped outer surface (15) with a flowing shape, which together with an inner surface (16) of the housing (2) have a generally substantially rotationally symmetrical, for instance cylindrical, medium passage space (17) with a radial dimension of at most 0.4x the radius of said outer surface (15), in which medium passage space (17) a number of angularly equidistant stator blades (18) bounding pair stator blades (19) are accommodated, which stator blades (19) each their end zone (20), which faces a rotor (8), forming a fifth medium passage (24), has a direction which deviates substantially, in particular at least 60 °, from the axial direction (21), and on their other, a sixth The end zone (22) forming the medium passage (25) has a direction which deviates slightly, in particular at most 15 °, from the axial direction (21); which fifth medium passages (24) for medium flow substantially in the axial direction connect to the fourth medium passages (11), and are placed in substantially the same radial positions, and which sixth medium passages (25) are connected stand with the at least one second medium throughput (4) (5) (6); (c.2) a second central body, between the sixth medium throughput (26) and the at least one second medium throughput (4) (5 ) (6) a plurality, running from the sixth medium passages (26) towards the at least one second medium pass (4) (5) (6), through the outer surface (29) of the second central body (23) and extending the cylindrical inner surface (16) of the housing (2) bounded manifold channels (26), a general medium flow path 15 (27) being defined between the first medium passage (3) and the at least one second medium passage (4) ( 5) (6) through the first medium passage (3), the third media passages (9), rotor channels (10), fourth media passages (11), stator channels (18), 20 sixth media passages (25), manifold channels (26), second media passages (4) (5) (6), and vice versa, with substantially smooth and continuous transitions between said parts during operation; and wherein the structure is such that during operation there is a mutual force coupling between the rotation of the rotor (8), and thus the rotation of the shaft (7), on the one hand, and the pressure in the said medium flow path (27). flowing medium. wherein the rotor (517) and the stator (518) of the rotary device in a concentric relationship are dual for pumping a first gas stream (519) from the first pump inlet (512) via two respective separate gas flow paths (519,520) the first inlet (506) and a second gas flow (520) from the second pump inlet (515) to the second inlet (509), which rotor shaft (524) is drivable by a motor (525). o o y i 3 ^ A gas compressor (501), comprising: a housing (502) with a gas inlet (503) and a gas outlet (504); a first compression space (505) present in that housing (502) with a first inlet (506) and first outlet (507); a second compression space (508) provided in that housing (502) with a second inlet (509) and a second outlet (510); 10 a first gas pump (511) with a first pump inlet (512) connecting to the gas inlet (503) and first pump discharge (513); a second gas pump (514) with a second pump inlet (515) and a second pump discharge (516); 15 a first check valve (522) arranged between the first pump discharge (513) and the first inlet (506); a second check valve 20 (523) disposed between the second pump discharge (516) and the second inlet (509); which first and second gas pumps (511,514) are integrated and are configured jointly as a rotary device (1), comprising: (a) a housing (2) with a central, substantially axial first medium passage (3) and at least one substantially axial second fluid passage (4) (5) (6); (b) a rotor shaft extending in that housing (2) and outside that housing (2), which is rotatably mounted relative to that housing (2) and a rotor (8) accommodated in that housing (2) which rotor (8) connects to said first medium passage (3) with a central third medium passage (9), which third medium passage (9) branches in a number of angularly equidistant rotor channels (10), each of which extends in a respective at least The gas compressor of claim 1, wherein the volume of the first compression space (505) is greater than the volume of the second compression space (508). Gas compressor according to claim 1, wherein a non-return valve (522,523) comprises two resilient annular lips which cooperate with their free downstream ends in a substantially sealing manner. Gas compressor according to claim 1, wherein the axial section of each rotor channel has a shape which more or less corresponds to a half cosine function. Gas compressor according to claim 1, wherein the number of rotor channels is at least 10. Gas compressor according to claim 8, wherein the number of rotor channels is at least 20. Gas compressor according to claim 6, wherein the number of rotor channels is at least 40. 8. Gas compressor as claimed in claim 1, wherein the number of rotor channels deviates from the number of stator channels such that position coincidence of the fourth medium passages and the fifth medium passages during rotation is absent and thus associated periodic pressure fluctuations in the medium flowing through the rotation device become appearance. Gas compressor as claimed in claim 1, wherein an input propeller with a number of propeller blades is arranged in the third medium feed-through serving as medium inlet. 10. Gas compressor according to claim 1, wherein the rotor comprises two plates which, together with partitions also serving as spacers, delimit the rotor channels. 11. Gas compressor as claimed in claim 1, wherein the partitions extend from the third medium passage to a zone remote from the fourth medium passages co-limiting the trays. 1 0 0 3 7 5 5 Gas compressor according to claims 9 and 10, in which each propeller blade connects to a bulkhead. 13. Gas compressor according to claim 10, wherein a first group of first baffles extends from the third medium throughput to the fourth medium throughput and at least one second group of second baffles is interlaced therewith, said second baffles extend from a position remote from the third media throughput to the fourth media throughput. A gas compressor according to claim 10, wherein the angle between a set of stator vanes forming a stator channel together in an area between the fifth medium throughput and the sixth throughput reaches a maximum value of at most 20 °. Gas compressor according to claims 13 and 14, wherein said angle reaches a maximum value of at most 10 °. 16. Gas compressor as claimed in claim 10, wherein the dishes and the partitions consist of plate material, for instance optionally fiber-reinforced plastic, aluminum (alloy), stainless steel or spring steel. Gas compressor according to claim 1, wherein all surfaces in contact with medium are resistant to chemical and / or mechanical action by the medium. A gas compressor according to claim 1, wherein all medium-contacting surfaces are made of such materials and are electrically conductively bonded together that sparking is effectively prevented. Gas compressor according to claim 1, wherein all surfaces that come into contact with medium have been pre-smoothed, for example by grinding, polishing, honing or applying a coating of, for example, a carbide, a nitride (eg titanium nitride or boron nitride), glass , a silicate, high-quality plastics, such as a polyimide. ... V O Gas compressor according to claim 16, wherein the ratio between the rotor diameter and the thickness of the sheet material has a value of 50-1600. 21. Gas compressor according to claim 10, wherein the partitions are coupled to the dishes by (spot) welding, gluing, soldering, magnetic forces, by means of screw connections, lip / hole connections, or the like. 22. Gas compressor according to claim 1, wherein the stator vanes consist of sheet material, for instance optionally fiber-reinforced plastic, aluminum (alloy), stainless steel or spring steel. The gas compressor of claim 1, wherein the thermal expansion coefficients of the materials of the cylindrical inner face of the housing and of the stator vanes are substantially equal. A gas compressor according to claim 23, wherein at least the cylindrical inner surface of the housing consists of the same material as the stator vanes. Gas compressor according to claim 1, wherein the stator channels are formed such that the distances between their opposing walls in a circumferential plane extending transversely of the axial direction are substantially equal at each axial position. 26. A gas compressor according to claim 1, wherein the shaft is solid and thus makes a substantial contribution to the mass moment of inertia of the rotatable unit comprising this shaft and said rotor. 27. Gas compressor according to claim 10, wherein the dishes are formed of metal by deep drawing, rolling, forcing, hydroforming, explosive deformation, by means of a rubber press, or the like. 28. A gas compressor according to claim 10, wherein the trays are formed of plastic by injection molding, thermoforming, thermo-vacuum forming or the like. 29. A gas compressor according to claim 1, wherein the rotor is made of sheet metal, which is laid on top of each other in at least two layers in a mold with a mold cavity with a shape corresponding to the desired shape of the rotor, between which two layers of pressurized medium are permitted to expand the sheet material against the wall of said mold cavity under plastic deformation to form the rotor. 30. Gas compressor according to claim 1, in which the shaft is rotatably mounted with respect to the housing in bearings which are located at such a great distance from the medium flow path that any temperature of the flowing medium, if any, which is greatly increased or decreased, has no or only negligible affects the temperature of those bearings. 31. A gas compressor according to claim 1, wherein the rotor is sealed from the housing by at least two labyrinth seals, one of which is in the region of the third medium throughput and the other in the of the fourth medium throughput . The gas compressor according to claim 1, wherein the number of stator vanes is at least 10. The gas compressor of claim 32, wherein the number of stator vanes is at least 20. 34. A gas compressor according to claim 1, wherein the ratio between the total cross-sectional area of all fourth medium passages and the third medium pass-through is at least 1. 35. A gas compressor according to claim 34, wherein the ratio between the total cross-sectional area of all fourth medium passages and the third medium pass-through is at least 3. The gas compressor of claim 35, wherein the ratio between the total cross-sectional area of all fourth medium passages and the third medium pass-through is at least 10. The gas compressor according to claim 1, wherein the ratio between the diameter of the ring of the fourth medium passages and the diameter of the third medium passage is at least 1.5. a! · "f 'V A gas compressor according to claim 37, wherein the ratio between the diameter of the ring of the fourth medium passages and the diameter of the third medium passage is at least 10. The gas compressor according to claim 38, wherein the ratio between the diameter of the crown of the fourth medium passages and the diameter of the third medium passage is at least 20. ***** 1009756